Relativistic mechanical device

ABSTRACT

A mechanical device includes a prime mover, and a number of rotating masses. Each mass is rotated simultaneously around centers of rotation in two or three planes that are at right angles to each other. The device includes one or more timing devices that are synchronized. The timing devices fix the relationship of the two simultaneous input rotations. In this device, internal energy creates an internal differential that is equalized by an external acceleration of the total mass, and internal energy is transferred to the exterior.

CROSS-REFERENCE TO RELATED APPLICATION

This application is a continuation-in-part of PCT Application No.PCT/US2011/051782, filed on Sep. 15, 2011, the entire contents beingincorporated by reference herein. This application also claims thebenefit of U.S. Provisional Application No. 61/383,132 filed on Sep. 15,2010, the entire contents being incorporated by reference herein.

BACKGROUND OF THE INVENTION

The term “classical physics” in the context of Einstein's Theory ofSpecial Relativity generally refers to Newtonian Physics, whichgenerally includes the branches of physics developed prior to thedevelopment of relativity and quantum mechanics. In general, classicalmechanics is based on Newton's Laws of Motion, which can be stated asfollows:

-   -   1. In the absence of a net force, a body is at rest or moves in        a straight line with constant speed.    -   2. A body experience a force F experiences an acceleration that        is related to F by F=ma, where m is the mass of the body.        Alternatively, forces equal to the time derivative of momentum.    -   3. Whenever a first body exerts a first force F on a second        body, the second body exerts a force −F on the first body. F and        −F are equal in magnitude and opposite in direction.

The “Theory of Relativity” (or “Relativity” by itself) generally refersto Albert Einstein's Theories of Special Relativity and GeneralRelativity. Einstein's Theory of Special Relativity is often expressedin terms of mass-equivalents or E=mc². According to the Principals ofRelativistic Mechanics, the energy and momentum of an object withinvariant mass M moving with a velocity v with respect to a givenreference frame are given by:

E=to γ mc2 p=γ mv

respectively.Where γ (the Lorentz factor) is given by:

$\gamma = {\frac{1}{\sqrt{1 - \left( {v/c} \right)^{2}}}.}$

The effects that are introduced by the theory of special relativity arewholly unfamiliar to human experience, and the theory itself has aspectsthat are in conflict with human logic. Yet, all the effects are real andcan be measured. Our understanding of the dynamics that create theserelativistic effects may be enhanced by a mechanical device thatdemonstrate the internal dynamics responsible for these effects.

BRIEF SUMMARY OF THE INVENTION

A mechanical device consisting of a prime mover, and a number ofrotating masses. Each mass is rotated simultaneously around centers ofrotation in two or three planes that are at right angles to each other.Another part of the device consists of one or a number of timing devicesthat are all synchronized. These timing devices fix the relationship ofthe two simultaneous input rotations. One of these rotations has avariable angular velocity, the other can have a constant or variablevelocity in a cycle of 360°. In the Lorentz equationγ=1/(1−(v/c)²)^(1/2). The constant “c” is normally defined as the speedof light in this context. However, its meaning herein has beenbroadened, and c is defined herein to be “THE UNIT GOVERNING VELOCITY OFA DYNAMIC SYSTEM,” and represents the constant angular input velocity ofa timing device according to the present invention. The Lorentz equationγ=1/1−(v/c)²)^(1/2) forms the mathematical basis for the timing deviceof the present invention, and (1 (v/c)²)^(1/2) is the cosine if v/c isdefined as the sine of the angle that resides between the two vectorsnamely the hypotenuse and the cosine vector of a right angle trianglethat occurs twice in one rotation of the timing device. The cosine ofthat angle is the inverse of a Lorentz factor. In a mechanical devicethe numerical magnitude of that factor is a result of the internaldimensional relationships. Special relativity uses the Lorentz factor toderive the relative mass or resisting force. External energy istransferred to the interior. In this device the opposite occurs,internal energy creates an internal differential that is equalized by anexternal acceleration of the total mass. Internal energy is transferredto the exterior.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partially schematic elevational view of a device accordingto a first aspect of the invention;

FIG. 1A is a partially schematic elevational view of a device accordingto another aspect of the invention;

FIG. 1B is a partially schematic elevational view of a portion of thedevice of FIG. 1A;

FIG. 2 is a schematic view of a single stage timing device utilized inthe device of FIG. 1;

FIG. 3 is a partially schematic isometric view of a timing device at 0°and 360° positions;

FIG. 4 is a partially schematic isometric view of the timing device ofFIG. 4 at a 180° position;

FIG. 5 is a partially schematic of a mechanical version viewed along theZ-axis;

FIG. 6 is a mechanical version viewed along the X axis;

FIG. 7 is an isometric view of a three-ringed coupling;

FIG. 8 is a relativistic curve a mass describes when subjected to a 45°relative angle of a single-stage timing device;

FIG. 9 shows the relative dimensions and motions of the centers ofrotation of the relativistic curve;

FIG. 10 is the geometric and dynamic relation the mass is subjected towhen it is at point E on the relativistic curve; and

FIG. 11 is the geometric and dynamic relationships the mass is subjectedto it is at point L.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

For purposes of description herein, the terms “upper,” “lower,” “right,”“left,” “rear” “front,” “vertical,” “horizontal,” and derivativesthereof shall relate to the invention as oriented in FIG. 1. However, itis to be understood that the invention may assume various alternativeorientations and step sequences, except where expressly specified to thecontrary. It is also to be understood that the specific devices andprocesses illustrated in the attached drawings and described in thefollowing specification are simply exemplary embodiments of theinventive concepts defined in the appended claims. Hence, specificdimensions and other physical characteristics relating to theembodiments disclosed herein are not to be considered as limiting,unless the claims expressly state otherwise.

A base relativistic unit may consist of two directional units, (one ofthese units is shown in FIG. 1) one rotating clockwise and the otherrotating counterclockwise. A directional unit consists of two massunits, one rotating clockwise and one counterclockwise. All rotations ofall masses are timed the same by one or more timing devices. While itcan be shown that the requirements of relativity can be satisfied withsimultaneous input rotations of a mass in two planes and a timingdevice, the possibility of providing a third simultaneous input rotationis not excluded.

With reference to FIG. 1, a directional unit according to one aspect ofthe present invention includes a frame 11 having an upper portion 12 anda lower portion 13 that are structurally interconnected as shownschematically by dashed line 14. A first shaft 15 is rotatably mountedto the lower portion 13 of frame 11 by a bracket 16 and ball bearings17. The first shaft 15 is operably interconnected, by shafts and gearsto a power source 18. Power source 18 may comprise an electric motor orother device having a rotating output shaft 19 that is operablyinterconnected to the first shaft 15. A second shaft 20 is rotatablymounted to the lower portion 13 of frame 11 for rotation about avertical axis 25. As discussed in more detail below, vertical axis 25comprises the primary center of rotation of directional unit 10. In theillustrated example, the second shaft 20 is rotatably mounted to lowerportion 13 of frame 11 by ball bearings 21, and the second shaft 20 isoperably interconnected with first shaft 15 by gears 22 and 23, suchthat powered rotation of first shaft 15 results in rotation of secondshaft 20 about vertical axis 25.

A primary rotor 30 includes a rigid upper structure 31, a lower rigidstructure 32, and one or more vertically extending rigid interconnectingstructures 33. The lower structure 32 is rotatably interconnected withsecond shaft 20 by ball bearings 34, and upper structure 31 is rotatablyinterconnected with upper portion 12 of frame 11 by a pin or shaft 35and ball bearings 34. Thus, primary rotor 30 rotates about vertical axis25 relative to frame 11, as shown by the arrow 36.

Directional unit 10 also includes a vertical shaft 40 that is rotatablyinterconnected to upper structure 31 of primary rotor 30 by a ballbearing 41. The vertical shaft 40 is rotatably interconnected tointerconnecting structure 33 of primary rotor 30 by a bracket 42 andball bearing 43. Thus, shaft 40 rotates relative to primary rotor 30about a vertical axis 45. Vertical axis 45, in turn, rotates aboutvertical axis 25 as primary rotor 30 rotates relatively to frame 11.

Vertical shaft 40 is operably interconnected with second shaft 20 by athree-ring coupler or coupling 50. With further reference to FIG. 7,three-ring coupler 50 includes input/output shafts/connectors 51 and 52that are operably connected by rings 53, 54, and 55. Shaft 51 is rigidlyinterconnected to ring 53 and shaft 52 is rigidly interconnected to ring55. Ring 53 is operably interconnected with ring 54 by arms 56-58. Eacharm 56-58 has opposite ends that are pivotally interconnected with rings53 and 54. Ring 54 is interconnected to ring 55 by arms 59-61 in asimilar manner. Due to the manner in which the rings 53-55 areinterconnected by the arms 56-61, shafts 51 and 52 must rotate at thesame angle or velocity and torque transmitted to either shaft 51 or 52is transmitted to the other of the two shafts 51 and 52. Shaft 51rotates about an axis 62 that is parallel to an axis 63 about whichshaft 52 rotates. In general, the axes 62 and 63 may be offset by adistance or dimension 65 that is normal to the axes 62 and 63. Thedistance 65 may vary depending upon the positions of the rings 53-55.Various three-ring couplers utilizing the same general configuration asthe three-ring coupler 50 shown in FIG. 7 are known in the prior art,such that further details concerning the three-ring coupler 50 are notbelieved to be required.

Referring again to FIG. 1, shaft 52 of three-ring coupler 50 is fixed tosecond shaft 20, and shaft 51 of three-ring coupler 50 is fixed tovertical shaft 40. Thus, vertical shaft 40 rotates at the same angularvelocity as second shaft 20. A gear 68 is fixed to vertical shaft 40 andmeshingly engages a gear 69 to thereby cause gear 69 to rotate about anaxis 70. Similarly, a gear 72 is fixed to shaft 40, and drives a gear 73for rotation about an axis 74. The axes 70 and 74 are normal to the axis45 of shaft 40. A mass 76 is connected to axis/shaft 70 by an arm 77,such that it rotates as shown by circle 80. Similarly, a mass 78 isconnected to axis/shaft 74 by an arm 79 and rotates as shown by circle81.

A shaft 85 is also operably connected to power source 18 to providerotation to shaft 85. Shaft 85 is operably interconnected to shaft 35 bya timing device 90. So the relationship of a certain differential inangular velocities, between shaft 35 and shaft 15, are alwaysmaintained. The location of the timing device shown in FIG. 1 is one ofthe possible locations. It could also be located on the frame near thepower source and serve two or more directional units 10. With furtherreference to FIGS. 3 and 4, timing device 90 includes an input shaft 91that is rigidly connected to a first arm 92. An output shaft 93 isrigidly connected to a second arm 94 having an elongated slot 95. Slot95 may be linear, or it may be curved or be wave-like in order toinfluence the angular velocity of the mass in a particular plane atcertain areas of its path. A pin or shaft 96 is rigidly connected tofirst arm 92, and a roller 97 is mounted on pin 96 for reciprocatingmotion within slot 95 of arm 94. When the output shaft 93 is at 0° or360° relative to input shaft 91, the timing device 90 is oriented asshown in FIG. 3. The movement of roller 97 in slot 95 is shown by thearrow 98.

With further reference to FIG. 2, AV1 is the input angular velocity, andit has a constant angular velocity. AV2 is a constantly changing angularvelocity within a cycle of 360°. It will be understood that there is no“start” of a cycle, just as there is no “start” to a circle. The maximumangle differential that occurs between arm C and A (FIG. 2) is therelativistic angle of the unit and it occurs when the angle δ=90° or270°. These are the only points in time in each cycle of 360° whereAV1=AV2. The maximum differential between the angular velocities AV1 andAV2 occurs when δ=180° and β=0°. Both arms A and C (FIG. 2) (arms 92 and94 in FIGS. 3 and 4) are angularly aligned at 180° and at δ=0° and 360°.

In FIG. 2, 100 designates the configuration of the device 90 as shown inFIGS. 3, and 101 designates the configuration shown in FIG. 4. 102designates a first intermediate position that is between theconfigurations of FIGS. 3 and 4 (i.e., between 0° and 180°), and 103designates a second configuration that is also between theconfigurations of FIGS. 3 and 4 (i.e., between 180° and 360°).

A timing device 90 may be used for each of the two simultaneous inputrotations. AV1 of the top timing device constitutes the “unit governingvelocity.” As shown in FIG. 1, one of the two rotations of the masses 76and 78 describing circles 80 and 81 is operably interconnected to shaft15, and shaft 35 is operably interconnected to rotate the Masses 76 and78 with the rotor around axis 25.

Masses 76 and 78 rotate in opposite directions (FIG. 1). In theillustrated example, mass 76 rotates in a clockwise direction, and mass78 rotates in a counterclockwise direction. However, the direction ofrotation of masses 76 and 78 could be switched, such that mass 78rotates in a clockwise direction, and mass 76 rotates in acounterclockwise direction. Mass 76, arm 77, and associated structureinterconnecting the first mass 76 to the vertical shaft 40 comprise afirst mass unit, and the second mass 78 and associated arm 79 and othercomponents comprise a second mass unit 84. The multiplicity of themasses serves only one of two basic purposes, to neutralize forces in acertain axis by complimentary interference or increases the frequency ofthe impulse if connected sequentially. The operation of the mass units82 and 84 will now be described in more detail in connection with FIGS.5 and 6.

The mass units 82 and 84 of FIG. 1 are shown schematically in FIGS. 6(X-Y Plane) and 7 (Y-Z Plane). Mass units 82 and 84 are substantiallythe same in operation (other than the direction of rotation of themass), such that only mass unit 82 is described in detail in connectionwith FIGS. 5 and 6. In FIGS. 5 and 6, a link 105 is rotatably mountedfor rotation about a primary axis or center of rotation 25. Thisrotation is the same as AV2 of the timing device 90 shown in FIG. 2. Thelink 105 of FIGS. 5 and 6 also corresponds to the primary rotor 30,including upper and lower structures 31 and 32 shown in FIG. 1. In FIGS.5 and 6 the mass center and arm 77 are provided with the angularvelocity of AV1. The mass center of rotation at 180° is designated 45Ain FIG. 6, and the mass center of rotation at 0° and 360° is designated45 in FIG. 6. Thus, it will be understood that the mass unit 82 of FIGS.5 and 6 is a somewhat simplified representation of the mass unitutilized to illustrate the operation of the mass units 82 and 84.

As shown in FIGS. 5 and 6, when the mass 76 is at 0° and 360° relativeto axes 45 and 25, the arm 77 is positioned in a “−Y” direction and thedistance between primary center 25 and mass 76 equals I+sin α. It willbe understood that the angle α is always the same angle in the trianglein the timing device and in the mechanical device described herein. Asdiscussed herein, the angle α is determined by the Lorentz factor.However, as the link 105 rotates about the primary axis or center ofrotation 25 (Z axis), the mass moves to the position designated 76A whenthe mass 76 is at 180° relative to the axis 45 and its relative distanceis only 1−sin α to the primary center 25. The relative frequency to 1that results when the mass 76 is at 180° is (1/(1−sin α))/(1+sin α) andrelative to the opposite side the relative frequency is:

((1/(1−sin α))/(1+sin α))^(1/2)=1/cos α

If v/c of the Lorentz equation 1/((1−(v/c)²)^(1/2) is sin α then ((1(v/c)²)^(1/2)=cos α. The Lorentz factor that is used for relative massin special relativity and the relative frequency factor of the devicecoincide when the relationships are the same. A relativistic devicealways features a relative unity and that unity can adopt any value,from one to infinity. However, the velocity it adopts can never beexceeded by any other velocity of a mass within that system. Also therelativistic factor 1/cos α once established is not influenced byvelocity.

FIGS. 5 and 6 show that the instantaneous centrifugal forces at theopposite 180° positions from the two simultaneous rotations in separateplanes 90° from each other are complimentary constructive in onedirection (direction 0°) and complimentary destructive in the otherdirection (direction 180°) relative to the primary center 25. It will beunderstood that FIGS. 5 and 6 are not intended to be conclusive withrespect to the sum of all directional forces during the time of acomplete cycle or one rotation nor is it intended to be conclusive as tothe direction or magnitude of the total force differential. It is merelyan indicator that a differential exists. A graphical representationconcerning what occurs during a complete cycle is shown in FIG. 8, asdiscussed below.

FIG. 8 shows a relativistic curve of a 45° relative angle α, where α isthe maximum angular differential of the two rotations of the timingdevice. The relative angular velocity AV1 was selected for rotation ofthe masses 76 and 78 describing circles 80 and 81 (FIG. 1).

The distances between points F & D and D & G define a relative frequencyof the device=(1/FD)/DG, and the effective relative frequency is I/cosα=√(1/FD)/DG=√(1/(1−sin α))*(1/(1+sin α)). T is the time center that isused in order to project the influence of the timing device on the pathof the mass. FIG. 8 shows the path a mass 76 or 78 has to follow whensubjected to the physical constraints of a single-stage timing device 90(see also FIG. 1). The path of the mass 110 as seen in the X-Y plane isshown in FIG. 8 by the curved line that passes through the points G, E,C, F, C1, E1, back to G. The relativistic curve shown in FIG. 8 occurswhen the primary rotation has a variable angular velocity. T is thecenter of the time circle and the driver of the total system.

Referring again to FIG. 8, the “normal” look of the egg-shaped circle110 is, in a sense, very misleading. The circle 110 actually consists offour individual curves 111, 112, 113, 114 each with its own relativeradius (distance) and relative frequency (angular velocity). There aretwo small transition areas just after position C and before position C′.(Going clockwise on the relativistic curve on FIG. 11) The path of themass encompasses 360°, but if the degrees of all the individual centersof rotation are added up, they seem to total 450°, the additional 90° or45° per side are due to the relativistic differential effect. The 450°is really a mirage, purely created by the additional 45° motion atposition C by the radial vector shown as member 77 in FIG. 5.

Two of the four curves 113 and 114 have the same radius and frequency.The centers of these four individual rotations are located in emptyspace. Their curves are formed by a projection from the two simultaneousmotions of the mass in three planes. None of these virtual centers ofrotation coincides with the real centers of rotation D and m in time(the real center of rotation m is a moving center and rotates aroundcenter D). These virtual centers of rotation seem to instantaneouslymove from one position to another, exerting no force whatsoever on themass due to that motion. (Motion in zero time) Therefore there is nochange in energy or velocity of the mass due to the change in radius,but the frequency will change inversely proportionally to the change inradius. Normally it would be expected that the frequency would increaseinversely proportional to the square of the relative distance. This isthe case when the mass moves towards the center of rotation. However,the difference here is that the center of rotation moves towards or awayfrom the mass.

FIG. 9 shows the relative dimensions and motions of the centers ofrotation of the relativistic curves segments and the relative motion ofthe mass. T is the center of the time circle that is the driver of thesystem, through the timing device and represents its relative unity,with a radius of 1 and a frequency of 1 and a mass of 1. As the masstravels from G to F on the relativistic curve the following motions arein evidence:

The center T of rotation, moves instantaneously to position M′ changingthe radius from 1 to 0.707 and the frequency from 1 to 1.414, but noteffecting the tangential velocity of the mass.

It must be understood, that for purposes of simplicity, the followingrepresentation has been idealized. The mass therefore has the followingproperties as it moves from G to E. All quantities are relative to 1:

The radius=0.707

The frequency=1.414

The time=1/1.414=0.707

The tangential velocity=1

The radial force=1²/0.707=1.414

The directional velocity in the +y direction at point E=I×0.707=0.707

The average −y directional force=1.414×0.707×4/π=1.2732

The relative directional −y momentum=1.2732×0.707=0.9

The center M′ of rotation of curve 111 moves instantaneously to positionK, changing the radius from 0.707 to 1.06 and the frequency to(0.707/1.06) 1.414=0.943, but not effecting the tangential velocity.

Part of the action occurs after the rotation in the z-y plane whenmember 77 of FIG. 5 completes 90° from position 0°. At that point member105 on FIG. 5 has only completed 54.735, therefore the mass is stillaccelerating radially towards the primary center D, in the +y directiondue to the tangential velocity, but starting to decelerate in the samedirection due to the rotation in the z-y plane that is now past 90°.Acceleration and deceleration have become complimentary destructiveuntil the rotation in the x-y plane has reached 90° and that is the sameposition as position C in FIG. 9. Due to the reduction in the radialforce the mass slowed down tangentially and directionally and reducedits frequency. This reduction in velocity and frequency is in evidenceat point C. With further reference to FIG. 9. The center K of therotation of curve 113 moves instantaneously to position N and the massdisplays the following relative properties at C:

The radius=0.5

The tangential frequency for the upper curvex=0.943×1.06/0.5=2

The +y directional velocity at C=0.5

The +x directional velocity at C=0.5

The tangential velocity of the mass at C=(0.5²+0.5²)½=0.707

With further reference to FIG. 9 and the geometry of the relativisticcurve FIG. 11, the center of rotation N moves to Point H at the sametime the mass moves from point C to point L. The motions were parallelto each other and there was no effect on the frequency or velocity ofthe mass, it constitutes a transition. In the curvature 112 forces fromthe radial and tangential rotation are complimentary destructive. Thisis responsible for the relativistic effect.

Properties of the xy Side, as the Mass Moves from Point L to Point F

The radius=0.5

The frequency=2

The time=0.5

The effective tangential velocity=0.707

The radial force=0.707²/0.5=1

The +y relative momentum=1×0.5+0.207=0.707 The above numbers areeffective numbers since the +y velocity that enters at point C is theonly velocity that can be translated. See geometric mechanicalcalculation on FIG. 10.

Since the effective arc in the −y and the +y direction are both 45° fromG to E and from L to F, the adjustment for the directionality factor of0.9 of the radial force does not have to be accounted for in therelativistic calculation or number. But will have to be taken intoaccount when the relative numbers are converted into real numbers bygiving the unit real size, mass and frequency. Therefore,

The relative +y force=1

The relative +y directional momentum=1×0.707=0.707

The relative −y directional momentum=0.707×1.414=−1.000

The directional relative momentum differential is −0.293 This internaldifferential is opposed by the total mass of the unit and the mass it isattached to, providing an acceleration for the assembly. Therelativistic or Lorentz factor is 1/0.707=1.414

The purpose of this numerical example is to illustrate that all therelativistic properties have been successfully incorporated into amechanical device and are all in total agreement with those obtained byspecial relativity, when both have the same velocity relationships. Itfurther demonstrates that a relativistic propulsion device can bedesigned to meet a specific need just like any other mechanical device.

However it is to be understood that the invention may assume variousalternative combinations and proportionalities in addition to thosealready mentioned as follows:

A third input could be added in the third plane that would not changethe concept of the basic system but might be helpful in optimizing itsresults.

Four different combinations of rotation and distances are possibleresulting in four families of relativistic curves. One relativisticcurve of the first family has been shown and described in detail. Sinceall follow the same process, the general description of the others belowshould be considered sufficient.

Family 1

a) Relationships of angular velocities:

Mass center of rotation m constant. Primary center of rotation Dvariable.

b) Relationship of distances:

Distance between centers of rotation relative unity 1. Radius ofgyration of mass around mass center of rotation relative sin α,(relative to 1)

Family 2

a) Relationship of angular velocities:

Mass center of rotation m variable. Primary center of rotation Dconstant.

b) Same as FAMILY 1.

Family 3

a) Same as FAMILY 1.

b) Relationship of distances:

Distances between centers of rotation relative sin α. Radius of gyrationof the mass around the mass center of rotation unity 1.

Family 4

a) Same as FAMILY 2.

b) Same as FAMILY 3.

In devices where masses rotate in three planes, the mechanicalcombination of relationships are the same, but there are more possiblecombinations since three rotations are combined with three distances.Not all combinations are necessarily used for practical exploitation,but all are useful for scientific and research purposes.

With reference to FIGS. 1A and 1B, a directional unit 10A according toanother aspect of the present invention, includes a frame having upperportions 12A and 12B and lower portions 13A and 14A. These arestructurally interconnected as shown schematically by the dashed line15A. A first shaft 16A is rotatably mounted to the lower frame portion14A by ball bearings 17A and 19A. The first shaft 16A is operablyconnected to a power source 18A. Power source 18A may comprise anelectric motor or other device having a rotating output that is operablyconnected to shaft 16A. A miter gear 21A is keyed to the top of shaft16A and forms the lower gear of the differential assembly 20A. Theoperation of the differential assembly 20A is substantially similar todifferential assembly 20 described above. Shaft 16A is located on thevertical axis 25A that comprises the primary center of rotation of thedirectional unit 10A.

A primary rotor assembly 30A includes vertical struts 31A and 32A thatare joined by top plate 33A and lower plate 34A. To lower plate 34A isfastened a tubular extension 35A that extends into gear assembly 50A. Tothe top plate 33A is fastened shaft 36A that is operably connected tothe output angular velocity of the timing device 90A. The operation ofthe timing device 90A is substantially the same as timing device 90described above. Unit 10A includes four horizontal members 37A, 38A,39A, and 40A. Horizontal members 37A and 38A support mass unit 82A, andare rotated by the timing belt system 60A. Horizontal members 39A and40A support mass unit 84A that is rotated by timing belt system 61A. Themass unit 84A and timing belt system 61A are substantially the same asthe corresponding components described above.

A shaft 85A is also connected to power source 18A to provide rotation toshaft 85A. Shaft 85A is operably interconnected to shaft 36A by a timingdevice 90A. Thus, the relationship of a certain differential in angularvelocities, between shaft 36A and shaft 16A, are always maintained atany given time in a rotation of 360°, regardless of the angular velocityof the power source.

If the timing device 90A is used for two simultaneous rotations in twoplanes as shown in FIG. 1A, one of the two rotations of the masses 76Aand 78A describing circles 80A and 81A is connected to the angularvelocity of AV1 and the rotation to AV2. Masses 76A and 78A rotatearound axis 25A.

Masses 76A and 78A rotate in opposite directions. In the illustratedexample, mass 76A rotates in a clockwise direction, and mass 78A rotatesin a counterclockwise direction. However, the direction of rotation ofmasses 76A and 78A could be switched, such that mass 78A rotates in aclockwise direction, and mass 76A rotates in a counterclockwisedirection. Mass 76A, arm 77A, and associated components comprise thefirst mass unit 82A, and the second mass 78A and associated arm 79A andother components comprise a second mass unit 84A. The multiplicity ofthe masses serves only one of two basic purposes, namely to neutralizeforces in a certain axis by complimentary interference, or to increasethe frequency of the impulse if connected sequentially.

Referring again to FIG. 1A, shaft 36A of the primary rotor assembly 30Ais operably connected to the timing device 90A. The primary rotorassembly 30A rotates about axis 25A with a constant variable angularvelocity (AV2). Shaft 36A is rotatably supported by bearing 41A, inupper frame portion 12A, and bearings 42A and 43A in lower frame portion13A. Gear 51A, is mounted on the tubular extension 35A of the primaryrotor assembly 30A and meshes with gear 52A that is mounted on shaft53A.

The gear ratio between gear 51A and 52A is selected such that shaft 53Arotates at ½ the angular velocity of the primary rotor assembly 30A inbearings 54A, 55A in lower frame portion 13A. Gear 56A is mounted onshaft 53A and meshes with gear 57A with a gear ratio of 1 to 1. Gear 57Ais rotatably mounted with bearing 58A on tubular extension 35A. Thedifferential U frame 22A of the differential assembly 20A is rigidlyfastened to gear 57A and rotates at ½ of the angular velocity in thesame direction as the primary rotor assembly 30A. The differential Uframe 22A is provided with a shaft 23A rotatably mounted in bearings 24Aand 26A. Miter gear 27A is mounted on one side of shaft 23A and mesheswith miter gears 21A and 28A. Gear 28A is mounted on shaft 44A thatresides in the tubular extension 35A and is rotatably mounted on thelower end with bearing 59A located in the differential U frame 22A andat the upper end in bearing 45A located in lower plate 34A of theprimary rotor assembly 30A. A counter weight 29A is also mounted onshaft 23A with clearance provided between it and gears 21A and 28A tobalance the differential U frame assembly.

It will be understood that miter gear 27A will have an angular velocityof ½ the angular velocity of the primary rotor 30A plus the angularinput velocity of shaft 16A. Miter gear 28A and shaft 44A will then havean angular velocity of miter gear 27A plus the angular velocity of thedifferential U frame 22A or the angular velocity of the primary rotor30A plus the angular velocity of the shaft 16A.

Referring again to FIG. 1B, at the top end of shaft 44A is mounted mitergear 46A that meshes with miter gears 47A and 48A. Miter gear 47A ismounted on shaft 62A that is rotatably mounted in strut 31A of theprimary rotor 30A with bearings 63A and 63B. Miter gear 48A is mountedon shaft 64A that is rotatably mounted in strut 32A of the primary rotor30A with bearings 65A and 6B. Since miter gears 47A and 48A with theirshafts 62A and 64A, respectively, rotate also with the primary rotor 30Aaround axis 25A, the angular velocities of miter gears 47A and 48A andtheir respective shafts around their own axes is the angular velocity ofmiter gear 28A minus the angular velocity of the primary rotor 30A andtherefore is the same as that of shaft 16A.

As shown in FIG. 1B, timing belt pulleys 66A and 67A are mounted onshafts 62A and 64A respectively. Pulley 66A drives timing belt 68A andpulley 67A drives timing belt 73A. Timing belt 68A drives mass unit 82Avia pulley 75A mounted on shaft 70A. Shaft 70A is rotatably supported byhorizontal members 37A and 38A with bearings 70B, 70C, 70D, and 70E.Mass arm 77A (see FIG. 1A) supports mass 76A and is rigidly mounted toshaft 70A. Mass arm 77A supports mass 76A and is rigidly mounted toshaft 70A. Similarly, shaft 74A is rotatably supported by horizontalmembers 39A and 40A with bearings 74B, 74C, 74D, and 74E. Mass arm 79Asupports mass 78A and is rigidly mounted to shaft 74A.

Accordingly, it will be understood that the masses rotate simultaneouslyin two planes, in one plane with the variable angular velocity of shaft36A of the primary rotor and in the other plane with the angularvelocity of input shaft 16A.

The invention claimed is:
 1. A mechanical device, comprising: a frame; aplurality of masses, where each of the masses is provided with two orthree input rotations. a first input shaft rotatably mounted to theframe such that the first input shaft rotates about a primary axis; asecond input shaft rotatably interconnected to the frame; a motoroperably connected to at least a selected one of the first and secondinput shafts directly and the other through a timing-device for poweredrotation of the two input shafts; a rotor structure mounted rotatably tothe first input shaft and connected to the second input shaft forrotation about the primary axis; a third shaft rotatably connected tothe rotor structure and defining a secondary axis that is spaced-apartfrom the first axis to define a distance; a coupling device mechanicallyinterconnecting the first input shaft and the third shaft such that thefirst input shaft and the third shaft rotate at the same angular rate,and wherein the coupling device permits the rotor structure to rotatesimultaneously at a one angular velocity while ensuring that the firstinput shaft and the third shaft can rotate at a different angular rate.2. A mechanical device as set forth in claim 1, that when attached toanother object will provide thrust and propulsion for the assembly orcan be utilized for other means, wherein the necessary force isinternally created by an internal relativistic differential of forcesthat result from an interaction of simultaneous and timed angularvelocities of each mass around centers of rotation in different planes.3. A mechanical device as set forth in claim 1, wherein each of themasses rotate around rotational centers in two or more planessimultaneously, and wherein the rotations are within each other, andwherein one or more rotations have constantly variable angularvelocities such that time and distance in these dynamics are constantlyvariable quantities in each rotation and are repetitive in eachsubsequent rotation, and wherein time and distance are variablequantities that fulfill the requirements of relativity.
 4. A mechanicaldevice as set forth in claim 1, wherein each mass rotates simultaneouslyaround centers of rotation in three planes at right angles to eachother, and wherein energy and momentum are exchanged between the axes,and wherein the three simultaneous rotations in three planes arerelated, timed, and directionalized by one or more timing devices, andwherein masses relative to the other masses are synchronizedsequentially in time, in order to increase the frequency of the impulse.5. A mechanical device as set forth in claim 1, wherein the dynamics ofthe conservation of the angular momentum are utilized, but only allowsthe frequency to be the inverse of the relative distance instead theinverse square of the relative distance, and wherein distance isexchanged for angular velocity, and wherein the magnitude of theexternal relative directional momentum is controlled by a relativisticangle α, and wherein the relativisic angle is defined where twosimultaneous rotations, one radially and one tangentially, describe themaximum angle differential between them in one rotation, and wherein theangle differential is the angle that in turn determines the relativisticvalue of the device.
 6. A mechanical device that uses a processconsisting of dimensions and dynamics derived from the Lorentz equationwherein the factor c is defined as the governing velocity of a dynamicsystem and the mechanical device demonstrates relativistic phenomenasimilar to Special Relativity independent of the speed of light.
 7. Amechanical device, comprising: a frame; a plurality of masses, whereeach of the masses is provided with two or three input rotations. afirst input shaft rotatably mounted to the frame such that the firstinput shaft rotates about a primary axis; a second input shaft rotatablyinterconnected to the frame; a timing device; a motor operably connectedto the two input shafts, wherein at least a selected ore of the inputshafts is connected to the timing device. a rotor structure mountedrotatably to the first input shaft and connected to the second inputshaft for rotation about the primary axis; A vertical line through therotational center of the masses that are rotatably connected to therotor structure and defining a secondary axis that is spaced-apart fromthe first axis to define a distance; a coupling device mechanicallyinterconnecting the first input shaft, through other rotatable parts,with the center of rotation of the masses, and wherein the couplingdevice permits the rotor structure to rotate simultaneously at adifferent rate then the first shaft or the masses around the mass centerof rotation.
 8. A mechanical device as set forth in claim 7, that whenattached to another object will provide thrust and propulsion for theassembly or can be utilized for other means, wherein the necessary forceis internally created by an internal relativistic differential of forcesthat result from an interaction of simultaneous and timed angularvelocities of each mass around centers of rotation in different planes.9. A mechanical device as set forth in claim 7, wherein each of themasses rotate around rotational centers in two or more planessimultaneously, and wherein the rotations are within each other, andwherein one or more rotations have constantly variable angularvelocities such that time and distance in these dynamics are constantlyvariable quantities in each rotation and are repetitive in eachsubsequent rotation, and wherein time and distance are variablequantities that fulfill the requirements of relativity.
 10. A mechanicaldevice as set forth in claim 7, wherein each mass rotates simultaneouslyaround centers of rotation in three planes at right angles to eachother, and wherein energy and momentum are exchanged between the axes,and wherein the three simultaneous rotations in three planes arerelated, timed, and directionalized by one or more timing devices, andwherein masses relative to the other masses are synchronizedsequentially in time, in order to increase the frequency of the impulse.11. A mechanical device as set forth in claim 7, wherein the dynamics ofthe conservation of the angular momentum are utilized, but only allowsthe frequency to be the inverse of the relative distance instead theinverse square of the relative distance, and wherein distance isexchanged for angular velocity, and wherein the magnitude of theexternal relative directional momentum is controlled by a relativisticangle α, and wherein the relativisic angle is defined where twosimultaneous rotations, one radially and one tangentially, describe themaximum angle differential between them in one rotation, and wherein theangle differential is the angle that in turn determines the relativisticvalue of the device.